US3793848A - Gas compressor - Google Patents

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US3793848A
US3793848A US00309909A US3793848DA US3793848A US 3793848 A US3793848 A US 3793848A US 00309909 A US00309909 A US 00309909A US 3793848D A US3793848D A US 3793848DA US 3793848 A US3793848 A US 3793848A
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rotor
gaseous fluid
fluid
rotation
gas
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M Eskeli
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps

Definitions

  • the gas enters said cen- 0 earc l trifuge near axis of rotation, and leaves near axis of rotation, thus providing for low work input to the [56] References Clted compressor.
  • Gas to be compressed may be air
  • the UNITED STATES PATENTS coolant may be water. Leaving gas after compression 2,073,833 3/1937 Bothezat will have lower temperature than at compressor entry. 2,729,073 l/l956 Nielsen 2,754,660 7/1956 Morrison 62/402 3 Claims, 2 Drawing Figures GAS COMPRESSOR BACKGROUND OF THE INVENTION
  • This invention relates generally to devices for compressing air and other gases by employing centrifugal force to compress said gas, from a lower pressure to a higher pressure.
  • FIG. 1 illustrates a cross section of the compressor, seen from the side
  • FIG. 2 shows an end view of the unit with a section removed to show the interior construction of the rotor and housing.
  • gas enters the machine via entry 16, and passes to rotor 11 at entry port 21, and then passes within the said rotor to near the periphery of said rotor and is being compressed by centrifugal action by said rotor, with cooling being provided during compression by cooling coil'l2. After compression, said gas is returned to center of rotor and leaves rotor atexit l4. Coolant fluid is being supplied via coolant entry 17, and passes to rotor via shaft 19, to distribution conduit 13, and from there to heat exchanger coil 12, and from there back to passage in shaft, and to coolant exit 18.
  • rotor casing is rotor casing
  • 22 and 23 are rotor seals
  • rotor shaft bearing is thermal insulation applied to rotor divider
  • 24 is rotor vane to assure that said gas will rotate with said rotor
  • 15 is a vent opening from space between rotor and housing, said vent may be connected to a vacuum pump to evacuate said space and thus reduce drag on said rotor.
  • FIG. 2 an end view of the unit shown in FIG. 1, is illustrated. A section is removed from the unit to show interior details. 10 is casing, 11 is rotor, 13 is coolant supply to heat exchanger 12, 24 is a radial vane within rotor cavity, 16 is inlet for gas, 19 is rotor shaft, 26 is unit base.
  • said gaseous fluid enters said rotor, near the axis of rotation, and is compressed within the rotor cavity by centrifugal action by said rotor on said gas, said compression being nearly isothermal, with cooling being supplied during compression by a heat exchanger provided within said rotor cavity.
  • said gaseous fluid After reaching rotor periphery, said gaseous fluid is passed on the other side of said rotor back to rotor center; thus, the work require to compress said gaseous fluid on entry side of said rotor, is nearly all recovered on the exit side of said rotor, with vanes placed within rotor cavity assuring that the gaseous fluid will rotate with rotor at all times.
  • the rotor cavity is sized to provide for relatively low gaseous fluid velocities, relative to rotor, typically these velocities in the area near the periphery are below feet per second.
  • the rotor tangential velocities at periphery are high, and may range from 500 feet per second upwards; these rotor velocities are dependent of the physical properties of the fluid being compressed, and the pressure required at rotor exit.
  • the rotor entry and exit openings may be the same diameter, or they may be different, as indicated in FIG. 1, or as required for pressure differential between rotor entry and exit.
  • the rotor side walls at rotor exterior may be built closely to rotor casing so that the space between rotor and wall may be partially evacuated by rotating thus reducing drag losses. Also, the space between rotor and casing may be evacuated by using a vacuum pump thereby eliminating losses due to friction on rotor outer surface.
  • this device can be used as an air compressor, or to compress gases or various kinds. Also, it can be used as the compressor stage in gas turbines and jet engines; also, it can be used as the basic unit to form a thrust generator by attaching a suitable nozzle to the rotor exit opening, so that the gas is accelerated to high velocity and then discharged.
  • Control for the unit may be provided by controlling the coolant flow, or by having a control valve either at rotor entry or exit.
  • the heat exchanger is shown in the drawings to be made of finned tubing loops placed within said rotor cavity. There are numerous other heat exchanger arrangements that can be used without departing from the spirit of the invention.
  • a device for compressing gases comprising:
  • a rotor for compressing said gas rotatably mounted and supported by a shaft and bearing, said rotor having an entry for said gaseous fluid near center of rotation, said rotor having passages built within to pass said gaseous fluid from said entry outwardly to rotor periphery and then to an exit near the center of rotation, said gaseous fluid being compressed within said rotor by centrifugal action by said rotor on said gaseous fluid to a higher pressure near the periphery of said rotor, and then said gaseous fluid being allowed to expand on the exit side of said rotor, vanes being provided in rotor cavity to assure that said fluid will rotate with said rotor, said gaseous fluid being cooled by a coolant fluid being supplied to said rotor and being circulated in heat exchange relationship with said gaseous fluid during compression, said coolant fluid being supplied to said rotor near axis of rotation and then being discharged from said rotor near axis of rotation, said rotor being rotated
  • a casing to support said rotor and to house said ro- 2.
  • the device of claim 1 wherein said casing is sealed to said rotor at areas near the center of rotation, and where said casing space between said casing and said rotor is evacuated by using a vacuum pump to reduce friction losses on said rotor.

Abstract

A method and apparatus for compressing gases, wherein a gas is compressed in a continuous flow centrifuge provided with cooling. The gas enters said centrifuge near axis of rotation, and leaves near axis of rotation, thus providing for low work input to the compressor. Gas to be compressed may be air, and the coolant may be water. Leaving gas after compression will have lower temperature than at compressor entry.

Description

I United States Patent [1 1 [111 3,793,848
Eskeli Feb. 26, 1974 [5 GAS COMPRESSOR 3,686,893 8/1972 Edwards .62/402 [76] In entor: Michael skel 0 Orchid Ln, 2,959,025 11/1960 Morrison 62/402 Dallas, Tex. 75230 Primary ExaminerWilliam J. Wye [22] Filed: Nov. 27, 1972 [21] Appl. No.: 309,909 [57] ABSTRACT A method and apparatus for compressing gases, [2%] 1.1.8.81. 62l glz2gd7g/(8lg wherein a gas is compressed in a continuous flow 'l 86 87 trifuge provided with cooling. The gas enters said cen- 0 earc l trifuge near axis of rotation, and leaves near axis of rotation, thus providing for low work input to the [56] References Clted compressor. Gas to be compressed may be air, and the UNITED STATES PATENTS coolant may be water. Leaving gas after compression 2,073,833 3/1937 Bothezat will have lower temperature than at compressor entry. 2,729,073 l/l956 Nielsen 2,754,660 7/1956 Morrison 62/402 3 Claims, 2 Drawing Figures GAS COMPRESSOR BACKGROUND OF THE INVENTION This invention relates generally to devices for compressing air and other gases by employing centrifugal force to compress said gas, from a lower pressure to a higher pressure.
Various devices for compressing gases using centrifugal force have been used in the past. In most conventional centrifugal compressors, the gas is compressed by accelerating said gas to a high velocity within a rotating impeller, and then discharging said gas to a stationary diffuser where the gas velocity is reduced with an accompanying increase in gas pressure. These devices generally are inefficient due to high friction losses and turbulence losses in the rotor passages and in the diffuser.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 illustrates a cross section of the compressor, seen from the side, and
FIG. 2 shows an end view of the unit with a section removed to show the interior construction of the rotor and housing.
DESCRIPTION OF PREFERRED EMBODIMENTS It is an object of this invention to provide a method and apparatus for compressing gases in a centrifugal machine wherein the energy required to compress said gas is partially supplied from external sources, and partially obtained from the gas being compressed, resulting in a compressor for which power input is low. Further, it is an object of this invention to provide a machine with a simple construction wherein gas velocities are low within the machine thus reducing friction losses.
In FIG. 1, gas enters the machine via entry 16, and passes to rotor 11 at entry port 21, and then passes within the said rotor to near the periphery of said rotor and is being compressed by centrifugal action by said rotor, with cooling being provided during compression by cooling coil'l2. After compression, said gas is returned to center of rotor and leaves rotor atexit l4. Coolant fluid is being supplied via coolant entry 17, and passes to rotor via shaft 19, to distribution conduit 13, and from there to heat exchanger coil 12, and from there back to passage in shaft, and to coolant exit 18. is rotor casing, 22 and 23 are rotor seals, is rotor shaft bearing, 27 is thermal insulation applied to rotor divider 25, 24 is rotor vane to assure that said gas will rotate with said rotor, and 15 is a vent opening from space between rotor and housing, said vent may be connected to a vacuum pump to evacuate said space and thus reduce drag on said rotor.
In FIG. 2, an end view of the unit shown in FIG. 1, is illustrated. A section is removed from the unit to show interior details. 10 is casing, 11 is rotor, 13 is coolant supply to heat exchanger 12, 24 is a radial vane within rotor cavity, 16 is inlet for gas, 19 is rotor shaft, 26 is unit base.
In operation, said gaseous fluid enters said rotor, near the axis of rotation, and is compressed within the rotor cavity by centrifugal action by said rotor on said gas, said compression being nearly isothermal, with cooling being supplied during compression by a heat exchanger provided within said rotor cavity. After reaching rotor periphery, said gaseous fluid is passed on the other side of said rotor back to rotor center; thus, the work require to compress said gaseous fluid on entry side of said rotor, is nearly all recovered on the exit side of said rotor, with vanes placed within rotor cavity assuring that the gaseous fluid will rotate with rotor at all times. There is a decrease in gaseous fluid pressure when the fluid passes from the rotor periphery to rotor exit at center of rotation, but this pressure loss is less than the pressure gain was on the entry side; thence, the unit exit pressure is higher than the unit entry pressure. Thermal insulation is placed on the rotor dividing wall to prevent heat being added to the cool gaseous fluid at the exit side of the rotor, as shown in FIG. 1, item 27. It should be noted that the gaseous fluid temperature is lower at unit exit, than at unit entry, and that the temperature of the leaving cooling fluid is higher than the temperature of the entering cooling fluid.
The rotor cavity is sized to provide for relatively low gaseous fluid velocities, relative to rotor, typically these velocities in the area near the periphery are below feet per second. The rotor tangential velocities at periphery are high, and may range from 500 feet per second upwards; these rotor velocities are dependent of the physical properties of the fluid being compressed, and the pressure required at rotor exit.
Power from an external source is supplied to rotor shaft 19.
The rotor entry and exit openings may be the same diameter, or they may be different, as indicated in FIG. 1, or as required for pressure differential between rotor entry and exit.
The rotor side walls at rotor exterior may be built closely to rotor casing so that the space between rotor and wall may be partially evacuated by rotating thus reducing drag losses. Also, the space between rotor and casing may be evacuated by using a vacuum pump thereby eliminating losses due to friction on rotor outer surface.
There are variety of applications that this device may be used. It can be used as an air compressor, or to compress gases or various kinds. Also, it can be used as the compressor stage in gas turbines and jet engines; also, it can be used as the basic unit to form a thrust generator by attaching a suitable nozzle to the rotor exit opening, so that the gas is accelerated to high velocity and then discharged.
Control for the unit may be provided by controlling the coolant flow, or by having a control valve either at rotor entry or exit.
Various controls, gages and governors may be used with the device of this invention. They do not form a part of this invention and are not further described herein.
The heat exchanger is shown in the drawings to be made of finned tubing loops placed within said rotor cavity. There are numerous other heat exchanger arrangements that can be used without departing from the spirit of the invention.
What is claimed is:
1. A device for compressing gases and comprising:
a. a rotor for compressing said gas, rotatably mounted and supported by a shaft and bearing, said rotor having an entry for said gaseous fluid near center of rotation, said rotor having passages built within to pass said gaseous fluid from said entry outwardly to rotor periphery and then to an exit near the center of rotation, said gaseous fluid being compressed within said rotor by centrifugal action by said rotor on said gaseous fluid to a higher pressure near the periphery of said rotor, and then said gaseous fluid being allowed to expand on the exit side of said rotor, vanes being provided in rotor cavity to assure that said fluid will rotate with said rotor, said gaseous fluid being cooled by a coolant fluid being supplied to said rotor and being circulated in heat exchange relationship with said gaseous fluid during compression, said coolant fluid being supplied to said rotor near axis of rotation and then being discharged from said rotor near axis of rotation, said rotor being rotated and supplied b. a casing to support said rotor and to house said ro- 2. The device of claim 1 wherein said casing is sealed to said rotor at areas near the center of rotation, and where said casing space between said casing and said rotor is evacuated by using a vacuum pump to reduce friction losses on said rotor.
3. The device of claim 1 wherein said gaseous fluid is air, and said coolant fluid is water.

Claims (3)

1. A device for compressing gases and comprising: a. a rotor for compressing said gas, rotatably mounted and supported by a shaft and bearing, said rotor having an entry for said gaseous fluid near center of rotation, said rotor having passages built within to pass said gaseous fluid from said entry outwardly to rotor periphery and then to an exit near the center of rotation, said gaseous fluid being compressed within said rotor by centrifugal action by said rotor on said gaseous fluid to a higher pressure near the periphery of said rotor, and then said gaseous fluid being allowed to expand on the exit side of said rotor, vanes being provided in rotor cavity to assure that said fluid will rotate with said rotor, said gaseous fluid being cooled by a coolant fluid being supplied to said rotor and being circulated in heat exchange relationship with said gaseous fluid during compression, said coolant fluid being supplied to said rotor near axis of rotation and then being discharged from said rotor near axis of rotation, said rotor being rotateD and supplied with power from an external source, said gaseous fluid pressure being lower at rotor entry than at rotor exit; said coolant being in separate passages within rotor; b. a casing to support said rotor and to house said rotor.
2. The device of claim 1 wherein said casing is sealed to said rotor at areas near the center of rotation, and where said casing space between said casing and said rotor is evacuated by using a vacuum pump to reduce friction losses on said rotor.
3. The device of claim 1 wherein said gaseous fluid is air, and said coolant fluid is water.
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Cited By (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3834179A (en) * 1973-10-11 1974-09-10 M Eskeli Turbine with heating and cooling
US3861147A (en) * 1973-10-09 1975-01-21 Michael Eskeli Sealed single rotor turbine
US3874190A (en) * 1973-10-30 1975-04-01 Michael Eskeli Sealed single rotor turbine
US3908396A (en) * 1973-06-20 1975-09-30 Carter James B Ltd Direct cycle heating, cooling and refrigerating apparatus
US4004553A (en) * 1974-03-25 1977-01-25 Alfa-Laval Ab Heat treating apparatus for liquids
US5931153A (en) * 1998-07-09 1999-08-03 Giebeler; James F. Apparatus and method for generating heat
US20080178588A1 (en) * 2004-10-12 2008-07-31 Guy Silver Method and system for generation of power using stirling engine principles
US20090025388A1 (en) * 2004-10-12 2009-01-29 Guy Silver Method and system for generation of power using stirling engine principles
US20100205960A1 (en) * 2009-01-20 2010-08-19 Sustainx, Inc. Systems and Methods for Combined Thermal and Compressed Gas Energy Conversion Systems
US20100224346A1 (en) * 2007-10-26 2010-09-09 Grundfos Management A/S Controlling transfer through one or more transferring elements
US20100229544A1 (en) * 2009-03-12 2010-09-16 Sustainx, Inc. Systems and Methods for Improving Drivetrain Efficiency for Compressed Gas Energy Storage
US7900444B1 (en) 2008-04-09 2011-03-08 Sustainx, Inc. Systems and methods for energy storage and recovery using compressed gas
US20110056368A1 (en) * 2009-09-11 2011-03-10 Mcbride Troy O Energy storage and generation systems and methods using coupled cylinder assemblies
US20110219763A1 (en) * 2008-04-09 2011-09-15 Mcbride Troy O Systems and methods for efficient pumping of high-pressure fluids for energy storage and recovery
US8046990B2 (en) 2009-06-04 2011-11-01 Sustainx, Inc. Systems and methods for improving drivetrain efficiency for compressed gas energy storage and recovery systems
US8104274B2 (en) 2009-06-04 2012-01-31 Sustainx, Inc. Increased power in compressed-gas energy storage and recovery
US8117842B2 (en) 2009-11-03 2012-02-21 Sustainx, Inc. Systems and methods for compressed-gas energy storage using coupled cylinder assemblies
US8171728B2 (en) 2010-04-08 2012-05-08 Sustainx, Inc. High-efficiency liquid heat exchange in compressed-gas energy storage systems
US8191362B2 (en) 2010-04-08 2012-06-05 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8225606B2 (en) 2008-04-09 2012-07-24 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US8234863B2 (en) 2010-05-14 2012-08-07 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8240140B2 (en) 2008-04-09 2012-08-14 Sustainx, Inc. High-efficiency energy-conversion based on fluid expansion and compression
US8240146B1 (en) 2008-06-09 2012-08-14 Sustainx, Inc. System and method for rapid isothermal gas expansion and compression for energy storage
US8250863B2 (en) 2008-04-09 2012-08-28 Sustainx, Inc. Heat exchange with compressed gas in energy-storage systems
US8272212B2 (en) 2011-11-11 2012-09-25 General Compression, Inc. Systems and methods for optimizing thermal efficiencey of a compressed air energy storage system
US8448433B2 (en) 2008-04-09 2013-05-28 Sustainx, Inc. Systems and methods for energy storage and recovery using gas expansion and compression
US8474255B2 (en) 2008-04-09 2013-07-02 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8479505B2 (en) 2008-04-09 2013-07-09 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8495872B2 (en) 2010-08-20 2013-07-30 Sustainx, Inc. Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas
US8522538B2 (en) 2011-11-11 2013-09-03 General Compression, Inc. Systems and methods for compressing and/or expanding a gas utilizing a bi-directional piston and hydraulic actuator
US8539763B2 (en) 2011-05-17 2013-09-24 Sustainx, Inc. Systems and methods for efficient two-phase heat transfer in compressed-air energy storage systems
US8567303B2 (en) 2010-12-07 2013-10-29 General Compression, Inc. Compressor and/or expander device with rolling piston seal
US8572959B2 (en) 2011-01-13 2013-11-05 General Compression, Inc. Systems, methods and devices for the management of heat removal within a compression and/or expansion device or system
US8578708B2 (en) 2010-11-30 2013-11-12 Sustainx, Inc. Fluid-flow control in energy storage and recovery systems
US8667792B2 (en) 2011-10-14 2014-03-11 Sustainx, Inc. Dead-volume management in compressed-gas energy storage and recovery systems
US8677744B2 (en) 2008-04-09 2014-03-25 SustaioX, Inc. Fluid circulation in energy storage and recovery systems
US8997475B2 (en) 2011-01-10 2015-04-07 General Compression, Inc. Compressor and expander device with pressure vessel divider baffle and piston
US20150107249A1 (en) * 2013-10-22 2015-04-23 Access Energy Llc Extracting Heat From A Compressor System
US9109512B2 (en) 2011-01-14 2015-08-18 General Compression, Inc. Compensated compressed gas storage systems
US9109511B2 (en) 2009-12-24 2015-08-18 General Compression, Inc. System and methods for optimizing efficiency of a hydraulically actuated system
US9540961B2 (en) 2013-04-25 2017-01-10 Access Energy Llc Heat sources for thermal cycles

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Cited By (67)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3908396A (en) * 1973-06-20 1975-09-30 Carter James B Ltd Direct cycle heating, cooling and refrigerating apparatus
US3861147A (en) * 1973-10-09 1975-01-21 Michael Eskeli Sealed single rotor turbine
US3834179A (en) * 1973-10-11 1974-09-10 M Eskeli Turbine with heating and cooling
US3874190A (en) * 1973-10-30 1975-04-01 Michael Eskeli Sealed single rotor turbine
US4004553A (en) * 1974-03-25 1977-01-25 Alfa-Laval Ab Heat treating apparatus for liquids
US5931153A (en) * 1998-07-09 1999-08-03 Giebeler; James F. Apparatus and method for generating heat
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US20080178588A1 (en) * 2004-10-12 2008-07-31 Guy Silver Method and system for generation of power using stirling engine principles
US20090025388A1 (en) * 2004-10-12 2009-01-29 Guy Silver Method and system for generation of power using stirling engine principles
US20100224346A1 (en) * 2007-10-26 2010-09-09 Grundfos Management A/S Controlling transfer through one or more transferring elements
US8479505B2 (en) 2008-04-09 2013-07-09 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8763390B2 (en) 2008-04-09 2014-07-01 Sustainx, Inc. Heat exchange with compressed gas in energy-storage systems
US8733094B2 (en) 2008-04-09 2014-05-27 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US8240140B2 (en) 2008-04-09 2012-08-14 Sustainx, Inc. High-efficiency energy-conversion based on fluid expansion and compression
US8250863B2 (en) 2008-04-09 2012-08-28 Sustainx, Inc. Heat exchange with compressed gas in energy-storage systems
US8225606B2 (en) 2008-04-09 2012-07-24 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
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US8627658B2 (en) 2008-04-09 2014-01-14 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US8359856B2 (en) 2008-04-09 2013-01-29 Sustainx Inc. Systems and methods for efficient pumping of high-pressure fluids for energy storage and recovery
US8474255B2 (en) 2008-04-09 2013-07-02 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8448433B2 (en) 2008-04-09 2013-05-28 Sustainx, Inc. Systems and methods for energy storage and recovery using gas expansion and compression
US8240146B1 (en) 2008-06-09 2012-08-14 Sustainx, Inc. System and method for rapid isothermal gas expansion and compression for energy storage
US8122718B2 (en) 2009-01-20 2012-02-28 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
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US7958731B2 (en) 2009-01-20 2011-06-14 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
US20110083438A1 (en) * 2009-01-20 2011-04-14 Mcbride Troy O Systems and methods for combined thermal and compressed gas energy conversion systems
US20100205960A1 (en) * 2009-01-20 2010-08-19 Sustainx, Inc. Systems and Methods for Combined Thermal and Compressed Gas Energy Conversion Systems
US8234862B2 (en) 2009-01-20 2012-08-07 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
US20110079010A1 (en) * 2009-01-20 2011-04-07 Mcbride Troy O Systems and methods for combined thermal and compressed gas energy conversion systems
US8234868B2 (en) 2009-03-12 2012-08-07 Sustainx, Inc. Systems and methods for improving drivetrain efficiency for compressed gas energy storage
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US8046990B2 (en) 2009-06-04 2011-11-01 Sustainx, Inc. Systems and methods for improving drivetrain efficiency for compressed gas energy storage and recovery systems
US8104274B2 (en) 2009-06-04 2012-01-31 Sustainx, Inc. Increased power in compressed-gas energy storage and recovery
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US8109085B2 (en) 2009-09-11 2012-02-07 Sustainx, Inc. Energy storage and generation systems and methods using coupled cylinder assemblies
US20110056368A1 (en) * 2009-09-11 2011-03-10 Mcbride Troy O Energy storage and generation systems and methods using coupled cylinder assemblies
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